JPH05149558A - Heat carrier - Google Patents

Abstract

(57) [Abstract] [PROBLEMS] The present invention relates to a heat transfer device that uses heat for heating or the like by utilizing a pressure increase when heating a refrigerant, and reduces a decompression start delay time in a liquid receiver. The purpose is to shorten the width to shorten the opening / closing cycle and to increase the heat transfer capacity. [Structure] A liquid receiver 5 provided above the gas-liquid separator 1 by connecting the refrigerant heater 2 and the gas-liquid separator 1 to an annular pipe line.
A drop pipe 7 having a first check valve 6 and a first opening / closing valve 8
With a pressure equalizing pipe 9 having a heat transfer portion 21 connected to the annular pipe line, a gas-liquid separator 1, a radiator 10, and a second on-off valve 2.
3, the liquid receiving device 5 has an annular circulation path 22 in which pipes are sequentially connected, and the second opening / closing valve 23 is arranged above the liquid receiving device 5 so that the space between the liquid receiving devices goes down from the outlet of the second opening / closing valve 23. An outlet pipe 24 that is a gradient pipe is provided.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat transfer device for utilizing heat for heating or the like by utilizing a pressure rise when heating a refrigerant.

[0002]

2. Description of the Related Art A conventional heat transfer device is disclosed in, for example, Japanese Patent Laid-Open No.
As shown in Japanese Patent No. 51631, the structure is as shown in FIG.

That is, the gas-liquid separator 1 is arranged above the refrigerant heater 2 and is connected by an inlet pipe 3 of the refrigerant heater 2 and an outlet pipe 4 of the refrigerant heater 2 and connected by an annular pipe line. ing. Further, the liquid receiver 5 is arranged above the gas-liquid separator 1, is connected to the gas-liquid separator 1 by a drop pipe 7 having a first check valve 6, and is further provided with a pressure equalizing pipe 9 having a first opening / closing valve 8. It is connected to the gas-liquid separator 1 via the outlet pipe 4. The gas-liquid separator 1 and the radiator 10 arranged on the indoor side as the use side are connected by a gas refrigerant forward pipe 11, and the radiator 10 and the liquid receiver 5 are liquid refrigerant return pipes having a second check valve 12. It is connected at 13. As described above, the gas-liquid separator 1, the radiator 10, the second check valve 12,
The liquid receiver 5 and the first check valve 6 form an annular circulation path which is sequentially connected by piping. Reference numeral 14 is a temperature detector provided in the outlet pipe 4 of the refrigerant heater 2, and 15 is a control device for controlling the opening / closing time of the first opening / closing valve 8 according to the temperature detected by the temperature detector 14. Reference numeral 16 is a burner provided in the refrigerant heater 2, and the burner 16 heats the refrigerant. 17 is a radiator 1
It is a blower installed in 0.

The operation of the above structure will be described below. In the refrigerant heater 2, the refrigerant heated by the combustion heat of the burner 16 flows into the gas-liquid separator 1 through the outlet pipe 4 in a two-phase state of gas and liquid, and the liquid refrigerant is heated again from the inlet pipe 3 by the refrigerant heating. Flows into the vessel 2. On the other hand, gas-liquid separator 1
The gas refrigerant of the two-phase state refrigerant that has flowed into the heat exchanger 10 enters the radiator 10 through the gas refrigerant forward pipe 11 and exchanges heat with the indoor air sent by the blower 17, condenses heat and condenses into supercooled liquid.

When the first opening / closing valve 8 is closed, the supercooled liquid refrigerant condensed and liquefied in the radiator 10 condenses the gas refrigerant from the liquid refrigerant return pipe 13 through the second check valve 12. As a result, it flows into the liquid receiver 5. At this time, receiver 5
Since the internal pressure is lower than the internal pressure of the gas-liquid separator 1, the first check valve 6 is closed. When the on-off valve 8 is opened in this state, the liquid receiver 5 and the gas-liquid separator 1 communicate with each other through the pressure equalizing pipe 9 to be in a pressure equalizing state, and the liquid refrigerant in the liquid receiver 5 undergoes the first check by gravity. It flows through the valve 6 into the gas-liquid separator 1.

Next, when the first on-off valve 8 is closed again, the first check valve 6 is closed, and the condensed subcooling liquid refrigerant of the radiator 10 flows into the liquid receiver 5 inside the liquid receiver 5. The cycle in which the liquid is sucked by the sudden pressure reduction and the liquid receiver 5 is filled with the liquid refrigerant is repeated. As described above, the natural circulation cycle between the gas-liquid separator 1 and the refrigerant heater 2 is based on the evaporated refrigerant pressure, and the supply of the liquid refrigerant from the liquid receiver 5 to the gas-liquid separator 1 and the refrigerant heater 2 is the first opening / closing. This is an intermittent operation cycle depending on the opening / closing cycle of the valve 8.

[0007]

In the above-mentioned conventional configuration, in order to carry out heat transfer by heating the refrigerant, the opening / closing operation cycle of the first opening / closing valve 8 is set as shown in FIG. It was necessary to consider the delay time T _l . That is,
Reduced pressure receiver 5 first on-off valve 8 from the open state with a delay of time T _l from the time t ₁ has Tsu switched to the closed condition occurs, the receiver tank 5 at decompression time T _r is the liquid refrigerant It is filled and the decompression ends. This depressurization start delay time T _l is because in addition to the heat capacity of the container itself of the liquid receiver 5, it takes time for the liquid refrigerant that has passed through the valve portion of the second check valve 12 to enter the liquid receiver 5. It was
The second check valve 12 is installed in a mounting posture in which the valve seat 19 is closed by its own weight as shown in FIG. That is, the inlet side of the fluid is directed downward and the outlet side is directed upward. (The arrow in FIG. 6 indicates the flow direction of the fluid.) The liquid refrigerant inlet of the liquid receiver 5 is positioned above the liquid receiver 5, and after the liquid refrigerant has flowed in, the liquid receiver is dropped by gravity (shower). It is more effective if it is dropped into a shape) to improve the contact with the gas refrigerant and enhance the direct heat exchange efficiency. Therefore, the second check valve 12 and the liquid receiver 5
Has an inverted U-shaped reverse trap portion 20 as shown in FIG.

In the reverse trap portion 20, although the liquid refrigerant finally exists when the first opening / closing valve 8 is closed, it becomes a gas refrigerant when it is opened. Therefore, immediately after the first on-off valve 8 is closed, the reverse trap portion 20 is a gas refrigerant, and therefore the liquid refrigerant that has passed through the valve seat 19 of the second check valve 12 when closed is sequentially passed through the reverse trap portion 20. After a certain time, the liquid drops into the receiver 5. The time delay until the liquid refrigerant falls into the liquid receiver 5 causes the decompression start delay time.

By the way, the depressurization time T _r is the time from when the liquid refrigerant flows into the empty receiver 5 until the liquid refrigerant finishes flowing, and the internal volume of the receiver 5 and the radiator 10 The opening time T _ON is determined by the flow path resistance to the container 5, and the opening time T _ON is the time when the liquid refrigerant drops into the gas-liquid separator 1 from the liquid receiver 5 which is full. 9 and drop pipe 7
It is determined by the flow path resistance of.

Therefore, the opening time T of the first on-off valve 8_ONAnd when closed
Interval T_OFFOpening / closing cycle T expressed as the sum of _S(T_S= T_ON+ T
_OFF) Is the closing time T_OFFDelay time to start depressurization
T_lDepends on (T_OFF= T_r+ T_l) It will be.

Since the depressurization start delay time T _l is relatively large, there is a restriction on the reduction of the closing time T _OFF , and the opening / closing cycle T
_Inevitably , _S must be set longer, and there was a constraint on increasing the heat transfer rate (heating capacity when used for heating).

The present invention is intended to solve the above-mentioned problems, and an object of the present invention is to shorten the opening / closing cycle T _S by greatly shortening the depressurization start delay time T _l to increase the heat transfer amount (heating capacity).

[0013]

In order to achieve the above object, the present invention provides a liquid receiver provided above the gas-liquid separator, in which a refrigerant heater and a gas-liquid separator are connected to an annular pipe line. The heat transfer part connected to the annular pipe line by the drop pipe having the check valve and the pressure equalizing pipe having the first opening / closing valve, the gas-liquid separator, the radiator, the second opening / closing valve, and the liquid receiver. The second opening / closing valve is arranged above the liquid receiver, and an outlet pipe is provided as a downward gradient pipe from the outlet of the second opening / closing valve to the liquid receiver. It is configured.

[0014]

According to the present invention, the liquid refrigerant having passed through the second on-off valve is caused to flow into the liquid receiver in a short time by the action of gravity due to the above structure, and the depressurization start delay time is greatly shortened.

The closing time of the first opening / closing valve is shortened by greatly shortening the depressurization start delay time, and the number of times of sucking / dropping the liquid refrigerant in the liquid receiver per unit time is increased by shortening the opening / closing cycle, and It is possible to increase the amount of circulation, increase the amount of refrigerant heating, and increase the heat transfer amount (heating capacity when used for heating).

[0016]

Embodiment An embodiment of the present invention will be described below with reference to FIG.

In FIG. 1, the same reference numerals as those in FIG. 4 denote the same members and have the same functions, and thus detailed description thereof will be omitted.
The different points will be mainly described.

Reference numeral 21 denotes a refrigerant heater 2 and a gas-liquid separator 1 connected to an annular pipe line, and a liquid receiver 5 provided above the gas-liquid separator 1 and a drop pipe 7 having a first check valve 6. , A pressure equalizing pipe 9 having a first on-off valve 8 and a heat transfer unit connected to the annular pipe line. 22 is a gas-liquid separator 1, a radiator 10,
It is an annular circulation path in which the second opening / closing valve 23 and the liquid receiver 5 are sequentially connected by piping.

The second on-off valve 23 is arranged above the liquid receiver 5 and is connected to the liquid receiver 5 by an outlet pipe 24 which is a pipe having a downward slope between its outlet and the liquid receiver 5. Reference numeral 25 denotes an inlet pipe provided on the fluid inlet side of the second opening / closing valve 23, and the outlet pipe 24 is provided below the inlet pipe 25.

Reference numeral 26 is a combustion amount varying device for varying the combustion amount of the burner 16, and 27 is a control electrically connected to the first opening / closing valve 8, the second opening / closing valve 23, the temperature detector 14, and the combustion amount varying device 26. It is a device.

In the above structure, the opening / closing operation of the first opening / closing valve 8 and the second opening / closing valve 23, the combustion in the burner 16 and the operation of the blower 17 heat the refrigerant to heat the heat transfer.

In the above heat transfer operation, the first opening / closing valve 8
When the liquid refrigerant in the liquid receiver 5 is dropped into the gas-liquid separator 1 by opening and closing the second on-off valve 23, the liquid receiver 5 is filled with the gas refrigerant generated in the refrigerant heater 2. The gas refrigerant is cooled by the inflow of the supercooled liquid refrigerant that has been liquefied by the radiator 10 due to the closing of the first opening / closing valve 8 and the opening of the second opening / closing valve 23, and the volume of the gas refrigerant is condensed and liquefied. Decrease sharply. Due to this sudden decrease in volume, new supercooled liquid refrigerant flows in at a stretch and sudden depressurization is maintained. When the liquid receiver 5 becomes full, the inflow of liquid refrigerant stops and the pressure returns to the original state.

Here, the inflow of the supercooled liquid, which gives a chance to first condense the gas refrigerant, is connected from the outlet of the second opening / closing valve 23 to the liquid receiver 5 by the outlet pipe 24 which is a down-gradient pipe. , Closing the first on-off valve 8 and the second on-off valve 2
With the opening of 3, the liquid refrigerant quickly flows into the liquid receiver 5 by the action of gravity.

That is, the on-off valve is switched as shown in FIG.
Time t₀Start delay time T from _l'Compared to conventional
Large shortening (T_l′ << T_l) Done, closing time T_OFF′ (T
_OFF′ = T_r+ T_l′) Is also shorter than before (T_OFF′ << T
_OFF), The opening / closing cycle T _S′ Is wider than conventional
Shortening (T_S′ << T_S)it can.

By greatly shortening the opening / closing cycle, the refrigerant circulation capacity is increased by increasing the number of times the liquid refrigerant is sucked and dropped in the receiver, and the heating amount in the refrigerant heater can be increased. When used for heating, the heating capacity can be increased.

By the way, when the decompression start delay time is not used for shortening the opening / closing cycle but is directed to increase the decompression time, the liquid receiver can draw the supercooled liquid refrigerant over time. Become. This means that the flow path resistance of the pipe connecting the radiator on the use side and the heat source side for heating may be large, and it becomes possible to connect a long pipe between the use side and the heat source side. The installation workability of this device is improved.

By providing the outlet pipe 24 of the second on-off valve 23 below the inlet pipe 25 provided on the inlet side,
The amount of the supercooled liquid refrigerant held on the inlet side of the second opening / closing valve 23 is increased, the inflow amount of the liquid refrigerant when the second opening / closing valve 23 is opened can be increased, and the decompression start delay time can be shortened.

Further, as shown in FIG. 3, the second opening / closing valve 23
As a result, the valve body 28 is seated 29
If the check valve 31 is urged by the spring 30 toward
It is easy to provide the outlet pipe 24 'below the inlet pipe 25', and it is not necessary to electrically connect the outlet pipe 24 'to the control device 27, so that cost reduction and reliability can be improved.

[0029]

As described above, the heat transfer device of the present invention has the heat transfer portion and the circulation path, and the second opening / closing valve is arranged above the liquid receiver to receive liquid from the outlet of the second opening / closing valve. Since the outlet pipes are installed as down-gradient pipes between the units, the decompression start delay time is shortened and the heat transfer amount (heating capacity when used for heating) is increased with the increase in refrigerant circulation capacity. The effect is that it can be converted.

Further, there is also an advantage that a long piping connection between the user side and the heat source side can be made possible by expanding the decompression time margin and the installation workability is improved.

[Brief description of drawings]

FIG. 1 is a system configuration diagram of a heat transfer device according to an embodiment of the present invention.

FIG. 2 is a pressure reduction characteristic diagram of a liquid receiver according to an embodiment of the present invention.

FIG. 3 is a sectional view of a second opening / closing valve portion according to another embodiment of the present invention.

FIG. 4 is a system configuration diagram of a conventional heat transfer device.

FIG. 5 is a decompression characteristic diagram of a liquid receiver in a conventional heat transfer device.

FIG. 6 is a sectional view of a second check valve in a conventional heat transfer device.

[Explanation of symbols]

 1 Gas-Liquid Separator 2 Refrigerant Heater 5 Liquid Receiver 6 First Check Valve 7 Falling Pipe 8 First Opening / Closing Valve 9 Pressure Equalizing Pipe 10 Radiator 21 Heat Transfer Section 22 Circulation Path 23 Second Opening / Closing Valve 24 Outlet Pipe

Claims (3)

[Claims] 1. A liquid receiver provided above the gas-liquid separator, wherein the refrigerant heater and the gas-liquid separator are connected to an annular conduit.
A heat transfer section connected to the annular pipe line by a drop pipe having a first check valve and a pressure equalizing pipe having a first on-off valve, the gas-liquid separator, a radiator, a second on-off valve, and the liquid receiving liquid. An annular circulation path in which the vessels are sequentially connected by piping, and the second
A heat transfer device in which an on-off valve is disposed above the liquid receiver, and an outlet pipe is provided as a down-gradient pipe between the outlet of the second on-off valve and the liquid receiver. 2. The heat transfer device according to claim 1, wherein the outlet pipe of the second opening / closing valve is provided below the inlet pipe provided on the inlet side thereof. 3. The heat transfer device according to claim 1, wherein the second on-off valve is a check valve that biases the valve body toward the valve seat by a force that overcomes the weight of the valve body.